Transmission mechanism.



H.- W. PELLOWS. TRANSMISSION MEGHANI-SM. APPLIUATION FILED s112128, 1910.

H. W. FELLOWS.

TRANSMISSION MEGHANISM. APPLwATI'oN FILED SBN. e, 1910.

.Am r

mm i? H. W. FELLOWS.

TRANSMISSION MEGHANISM,

APPLIOATION FILED SEPT. a, 1910.

Patented Oct. 10, 1911.

3 SHEETS-SHEET 3. U

UNTTED sTATEs PATENT oFFioE.

HUGH WILLIAM FELLOWS, OF LOS ANGELES, CALIFORNIA, ASSIGNOR TO FELLOWS DIRECT POWER TRANSMISSION COMPANY, OF LOS ANGELES, CALIFORNIA, A COR- PORATION OF ARIZONA TERRITORY.

TRANSMISSION MECHANISM.

Locales.

Specification of Letters Patent.

Patented Oct. 10, 1911.

Application 1ed September 8, 1910. Serial No. 581,098.

To all whom it may concern:

Be it known that I, HUGH VILLIAM FEL- Lows, a citizen of the United States, residing at Los Angeles, in the county of Los Angeles and State of California, have invented a new and useful Transmission Mechanism, of which the following is a specification.

In a previous patent of mine No. 954,384, dated April 5, 1910, I have shown a transmission gearing of a type embodying an in.- termittent grip device wherein it is possible to operate the driven shaft at any desired speed within certain limits, it being possible to secure an infinite number of speeds .varying from the maximum speed afforded b y the mechanism down to a standstill, the mechanism being especially adapted for moving a heavy load at comparatively slow speeds, that is to say, generally at speeds less than about fifteen miles per hour, for example.

This type of mechanism operates to best advantage under the comparatively slow speeds mentioned, and the main object of the present invention is to provide a transmission mechanism which will embody all of the advantages of the intermittent grip type of mechanism referred to and to afford means for running at much higher speeds, this object being accomplished by providing a driving mechanism in combination with the intermittent grip mechanism, whereby the two sets of mechanism are so interrelated that the intermittent grip mechanism may be operated for the slower speeds and the other mechanism may be automatically brought into operation during the adjustment of the speed at a point where the maximum practical speed of the intermittent grip mechanism is reached, so that for speeds above this point the other mechanism is operative.

Referring to the drawings z--Figure 1 is a plan view of the mechanism, the clutch being in section. Fig. 2 is a side elevation of the mechanism shown in Fig. 1. Fig. 3 is a view similar to Fig. 2 omitting the casing and showing another position of the mechanism in dotted lines. In this view part of the intermittent grip device is shown in section on line oe3-x3 Fig. 1. Fig. 4 is a side elevation, in detail, on a reduced scale of the bevel gear and clutch mechanism. Fig. 5 is a plan view of the device for reversely tween the driving shaft and driven shaft are two distinct driving mechanisms which are so interrelated that they coperate harmoniously in certain functions, as will be pointed out. One of these driving mechanisms consists of intermediate grip devices operated by an adjustable linkage for varying the stroke of the intermittent grip devices and correspondingly varying the speed of the driven shaft, while the driving shaft may rotate at a uniform speed. The shaft 1 is provided with bevel pinions 4 and 5, the pinion 4 meshing with a bevel gear 6 on shaft 3, and the pinion 5 meshing with a bevel gear 7 on the driven shaft 2, these gears being continually in mesh, but the pinions 4 and 5 are loose on the shaft 1 and either one may be rigidly connected thereto by a clutch mechanism consisting of a clutch drum 8 `fixed to the pinion 4 and a clutch drum 9 fixed to a sleeve 10 which operates the pinion 5. Cooperating with the clutch drum 8 is a cone 11, and cooperating with the clutch drum 9 is a cone 12, each cone having pivoted dogs 13 each dog 13 having an arm 14 and an arm 15. The arms 15 bear against stationary thrust pins 16 which lie in a sleeve 17, the latter being held against longitudinal movement by a collar 18 which is secured to the shaft 1 by a'taper pin 19. Sliding on the sleeve 17 and collar 18 is a sleeve 20, either end of which is adapted to be forced under the arms of dogs 13 to thereby tilt the dogs, whereby as the inner ends of arms 15 of the dogs fulcrum on the stationary thrust pins 16 it results in forcing the cone 11 or 12, as the case may be, into engagement with its drum 8 or 9.

The parts are so proportioned that before the sleeve 20 releases the 'dogs at either end it will tilt the dogs at the opposite end, so

the cone 11 is released from its drum 8, the shaft 1 will rotate the driven shaft 2 through the medium of pinion 5 `and bevel gear 7. l/Vhen the cone 11 is engaged with its drum 8 and the cone 12 disengaged from its drum 9, the pinion 4 will be caused to rotate with shaft 1 and intermediate shaft 3 will be driven through the medium of vbevel gear 6.

lframe 28, the latter being pivoted at 29 to the frame 30. The rook frameV 28 is adjusted by means of links 31 which are connecte'dy at 32 to the rock frame and at 33 are connected to arms 34 which project down from a rock shaft controlled by a hand lever 36.

As the cranks 21 rotate they operate the connecting rods 22 which in turn swing the arms 23, and as the arms 23 are swung lat-4 erally they in turn swing the arms 26, and the latter having a fixed fulcrum at 27 act i to cause a longitudinal movement of the arms 23, which results in oscillating the rockers 24. The amount of longitudinal movement imparted to the arms 23 depends upon the location of the pivotal point 27 upon which the arms 26 swing, and this is j varied by adjusting the frame 28 to the point desired. Thus when the point 27 is about on a line between the end of connecting `rods 22 and-fthe pivotalpoint 25,*When the'cranks 21 are at mid-stroke, practically no longitudinal motion will be imparted to the arms 23, and consequently substantially no oscillation at-such time is given to the rockers`24. By moving up the rock frame 28 from the position shown in Figs. 2 and 3, the arms26 will swing in such circles that longitudinal movement will be imparted to the arms 23 and a corresponding amount of oscillation given to the rockers 24. The amount of oscillation given depends upon the position into which the rock frame 28 is adjusted. Thus in Fig. 3 dotted lines show the position into which it may be adjusted to give the maximum stroke to the rockers 24.V v

Each intermittent grip device comprises ay disk"37 having a peripheral V-shaped -groove 38. Mounted on each side ofi-each diskV 37 are vtwo rockers 24 before'referred to, andjournaled between each tvvo pair of in Fig. 6, each wedge block having a square notch 42 which receives the squared portion of the shaft 39, the wedge block being detachably held thereon by a plate 43, as clearly shown in Fig. 6. The inner end of each wedge block is Wedgeshaped, as shown, but formed with a convex surface 44, the radius of which is somewhat greater than the total length of the wedge block, with the result that when the wedge blocks stand on a perfect radial line with the driven shaft 2, as in the position shown in Fig. 3, they will not contact with the walls of the V-shaped groove 38, but if their shafts 39 be rocked in either direction to tilt the wedge blocks accordingly, the wedge blocks will engage with the walls of the groove 38 on that side which is brought into contact with the groove, so that during the stroke of the rocker in one direction the engagement of the wedge blocks with the grooved disk will turn the disk, and during the return stroke of the wedge blocks they will slide idly in the reverse direction Without imparting movement to the grooved disk. Thus the grooved disks may be driven in either direction by tilting the wedge blocks or the rockers and wedge blocks may be oscillated without imparting any movement whatever to the disks when the wedge blocks are in neutral position, which is the position shown in Fig. 3. On one side of a rocker 24 is a shift ring 45 having projections 46 which lie directly under collets 47 on the shafts 39.

As shown in Fig. 2, a spring pressed plunger 48 protrudes from each lug 46 and engages a concave depression 49 formed on the inner face of the associated collet. A segmental gear 50l is formed on the side of the shift ring 45 and is engaged by aY gear 51 mounted on a short shaft 52 having an arm 53 with a pin 54 which rides in a groove 55 in a segmental shifter 56 which is carried on a shift rod 57 sliding in bearings 58 on the frame 30. Thusv by shifting t-he shift rod 57 the shift-ers 56 will be moved laterally of the intermittent grip devices and will thereby, through the medium of pins 54, rock the arms 53 and shafts 52, and through the medium of gears 51 and 50 rock the shift ring 45, and the rounded heads of the spring pressed plunger 48 acting in the recesses in the inner ends of collets 47 will rock the latter in a directionaccordingvto the direction in which' the 'shift rod 57 is actuated, and when the collets are thus turned they will, through t-he medium of shafts 39, tilt the wedge blocks accordingly. This shifting maytake place without interruptingthe oscillation of the rockers as the segment-al shifters 56V permit thejcontinuous movement of the pins 54.

In order to prevent the intermittent grip devices from being reversed, except when their stroke has been reduced to the minimum, a trip in the form of a pivoted lat-ch 59 is employed, as shown in Fig. 5, which is pivoted at G0, and its end engages in a notch 61 formed in the shift rod 57. The latch 59 lies clirect-ly under one of the arms of the frame 2S, as shown in Fig. 2, so that when the frame 28 is lowered to bring the parts to neutral position, the frame will strike the latch 59 and release its end from the notch G1 which will permit the shift rod 57 to be actuated to reverse the wedge blocks.

As shown in Figs. 4 and 7, the grooved collar 2O is engaged by a forked lever G2 which has an arm 63 with a notched end G4. Connected with arm 34 by a link 34 is an arm 65 having a pin 66 which is adapted to engage in the notched end of the arm 63 when the cone 12 is in engagement with its drum 9, at which time the shaft 1 drives the shaft 2 directly through the pinion 5 and gear 7, pinion 4 at such time being idle. By swinging forward the arm 65 the pin 66 acting in the notch 64 will swing the arm 63 and move the cone 12 out of clutch with drum 9 and move cone 11 into clutch with drum 8, but, as before explained, cone 1l will engage drum 8 before cone 12 is released, with the result that upon the clutching of cone 11 with drum 8 pinion 4 will commence to drive shaft 3 and the latter will operate the intermittent grip devices through the medium of the before described mechanism at a speed which is somewhat less than the speed at which the shaft 2 is driven by the gear 7. Continued movement, however, results in disengaging the cone 12 whereupon the driven shaft 2 will be driven bythe intermittent grip devices, and at this point the pin 66 passes out of the notch 64 and the further movement of the adjusting shaft 35 will not disturb the cone 11 from its engagement with drum S, but will simply act to adjust the position of the rock frame 28 to vary the stroke of the intermittent grip devices. During the return adjust-ment, as the intermittent grip devices are caused to operate at their maximum speed, the pin 66 again enters the notch 64, whereupon further movement result-s in engaging cone 12 with drum 9, thereby driving t-he driven shaft 2 again at a higher speed, and a slight further movement will disengage cone 11, whereupon the intermittent grip mechanism becomes idle,

Vith this invention the load may be started at a very slow speed by operating the intermittent grip mechanism and thus utilize the turning leverage to best advantage and after starting the speed can be gradually increased until the maximum which is practical for the intermittent grip mechanism and by continuing the adjustment for still greater speed, the clutches automatically operate to throw in the bevel gearing drive and throw out the intermittent grip mechanism. The momentary engagement of both clutches prevents any interruption in the transmission of power to the driven axle. Although the two clutches are in simultaneous engagement momentarily, it should be understood that at such time there is no interference between the two driving mechanisms, for the reason that the intermittent grip devices are so constructed that the grooved disks are capable of running freely at a speed faster than that of the oscillating wedges, so that when the two clutches are in simultaneous engagement the shaft 2 is driven by the pinion 5 and gear 7 at a higher speed than it would be driven by the intermittent grip devices, and at this time the grooved disks 37, being mounted on the driven shaft 2, run at a somewhat greater angular speed than the angular speed of the wedge blocks.

What I claim is 1. In a transmission mechanism, a driving shaft, a -driven shaft, an intermittent grip device on the driven shaft, an intermediate shaft, gearing between the driving and intermediate shafts, gearing between the driving and driven shafts, mechanism operated by the intermediate shaft for oscillating the intermittent grip device, and means for clutching either of said gearings with the driving shaft.

2. In a transmission mechanism, a driving shaft, a driven shaft, an intermittent grip device on the driven shaft, an intermediate shaft, gearing between the driving and intermediate shafts, gearing between the driving and driven shafts, mechanism operated by the intermediate shaft for oscillating the intermittent grip device, means for clutching either of said gearings with the driving shaft, and means for adjusting the oscillating mechanism and automatically operating said clutch means.

3. In a transmission mechanism, a driving shaft, a driven shaft, an intermittent grip device on the driven shaft, an intermediate shaft, gearing between the driving and intermediate shafts, gearing between the driving and driven shafts, mechanism operated by the intermediate shaft for oscillating the intermittent grip device, means for clutching either of said gearings with the driving shaft, means for reversing the operative relation of the intermittent grip device to the driven shaft, and means operating automatically to prevent the operation of said reversing means except at a certain position of the oscillating mechanism.

4. In a transmission mechanism, a driving shaft, a driven shaft at right angles thereto, an intermediate shaft parallel with the driven shaft, a bevel gear on the intermediate shaft and a bevel gear on the driven shaft, bevell pinions on the driving shaft meshing With the respective bevel gears, means for clutching either of said bevel pinions to the driving shaft, intermittent grip devices on the driven shaft, mechanism operated by the intermediate `shaft for oscillating the intermittent grip devices, and asingle controlling means for regulating the stroke of said oscillating means and operating said clutch mechanism to automatically cause simultaneous clutching of both bevel pinions to the driving shaft when moving said controlling device to release either bevel pinion from the driving shaft and clutch the other therewith.

In testimony whereof, I have hereunto set my hand at Los Angeles, California, this 26th day of August 1910.

HUGH WILLIAM FELLOVVS.

l Gr. T. HAGKLEY,

l?. H. SHELTON.

Copies of this patent may be obtained for five cents each, by addressing the Commissioner of Patents,

' Washington, D. C. 

